JP2010181003A - Transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To finish engagement ON/OFF operation in a short time and to prevent destruction of a transmission caused by clutch disengagement when excessive torque is applied. <P>SOLUTION: This transmission 10 includes: a pair of first gear elements 16 and a pair of second gear elements 17 as at least two pairs of gear elements, respectively arranged between an input shaft 12 and an output shaft 14 rotatably supported; a first clutch 40 and a second clutch 42 as at least two pairs of clutches, respectively releasably coupling at least the two pairs of gear elements between the input shaft and the output shaft; at least a pair of noncircular gear elements 18 arranged between the input shaft and the output shaft; and a clutch 44 for at least the pair of noncircular gear elements, releasably coupling at least the pair of noncircular gear elements between the input shaft and the output shaft. The clutch for the pair of noncircular gear elements is composed of a dog clutch configured to be engaged only on an inclined surface. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a transmission.

  At present, a large number of transmissions capable of changing the reduction ratio in multiple stages, such as an automatic transmission of an automobile, have already been developed and are becoming established machines. In this automobile transmission, there is a problem of efficiently transmitting power when changing the reduction ratio.

  Normally, gear pairs with different reduction ratios cannot be meshed and rotated at the same time, so the reduction ratio cannot be changed while supporting the load without stopping the rotation. Also, in a transmission such as a normal automobile, the rotational speed of the gear to be fastened is different from that of the shaft before changing the reduction ratio. A large slip occurs between them, it is difficult to accurately transmit the rotation angle, and power transmission efficiency is also poor.

  Therefore, by using a pair of non-circular gear elements and a clutch, the reduction ratio can be changed while supporting the load without stopping the rotation, the rotation angle can be accurately transmitted, and the power can be transmitted efficiently. A transmission that can be used has been proposed (Patent Document 1). As the clutch, a dog clutch generally used in a transmission of an automobile can be considered.

  For example, as shown in FIG. 10, the dog clutch includes symmetrical drive elements 71 and 72 on the same axis, for example, on the rotating shaft 70, and driven and driven (also referred to as driven) clutch elements. Each of the clutch elements 71 and 72 is provided with a plurality of long dog portions 74 whose tips are formed in a mountain shape with a predetermined gap 76 along the circumferential direction of the rotary shaft 70, and the dog portion 74 is one dog portion 74. Have sliding contact surfaces 73 that are in sliding contact with each other so as to fit in the gap 76 between the other dog portions 74.

  By the way, as a clutch used for a non-circular gear element pair, it is required to complete the ON / OFF operation of meshing in a short time, and it is desirable that the clutch is disengaged when an excessive torque is applied to the clutch.

International Publication No. WO2008 / 062718A1 Pamphlet

  However, since the dog clutch has a long engagement stroke of the dog portion 74, not only does it take time to turn on / off the engagement of the dog clutch, but the clutch does not disconnect even when excessive torque is applied to the dog clutch. Therefore, there is a risk of causing damage to the transmission including damage to the non-circular gear element pair.

  The present invention solves the above-described problems of the prior art, can complete the ON / OFF operation of meshing in a short time, and prevents the transmission from being broken by the clutch being disconnected when excessive torque is applied. An object of the present invention is to provide a transmission that can perform the above operation.

  The present invention provides at least two gear element pairs, a first gear element pair and a second gear element pair, which are respectively disposed between a rotatably supported input shaft and an output shaft; A first clutch and a second clutch which are at least two sets of clutches releasably connecting at least two sets of the gear element pairs between the shaft and the output shaft; the input shaft and the output shaft; At least one set of non-circular gear element pairs disposed between and at least one set of non-circular gear element pairs releasably connecting between the input shaft and the output shaft. A clutch for a circular gear element pair, wherein the non-linear gear element pair has a reduction ratio between the input shaft and the output shaft, and the first gear element between the input shaft and the output shaft. Said first gear element pair when the pair is connected A reduction ratio between the first engagement section that is equal to the first reduction ratio in at least a part of the engagement sections and the input shaft and the output shaft is between the input shaft and the output shaft. The non-circular gear element includes a second meshing section that is equal to a second reduction ratio in a meshing section of at least a part of the second gear element pair when the two gear element pairs are connected. The counter clutch includes a dog clutch configured to mesh with only a slope.

  The dog clutch is composed of a symmetric drive element and a driven clutch element facing each other on the same axis, and the clutch element includes a plurality of dog parts having a mountain-shaped convex part composed of two inclined surfaces along the circumferential direction of the shaft. By providing the two inclined surfaces of the adjacent dog portions, valley-shaped concave portions are formed, and convex portions and concave portions are alternately formed in the circumferential direction, and the convex portions and concave portions of the clutch element on the driving side are formed on the driven side. It is preferable that the clutch is configured to be turned on or off by being engaged with or separated from the concave and convex portions of the clutch element.

  Of the clutch elements on the driving side and the driven side, one clutch element has a dog portion arranged in an outer spline shape, and the other clutch element has a dog portion arranged in an inner spline shape. It is preferable that the ridge lines of the convex portions are formed to be inclined at the same angle.

  According to the present invention, the meshing ON / OFF operation can be completed in a short time, and the clutch can be disconnected when the excessive torque is applied to prevent the transmission from being destroyed.

It is a mechanism figure showing typically an example of a transmission to which the present invention is applied. It is a figure which shows typically the pitch circle or pitch curve of the gear of a transmission. (A) is a graph which shows typically the change of the reduction ratio of a non-circular gear pair, (b) is a table | surface which shows ON and OFF of a clutch. (A) is a graph which shows typically the change of the reduction ratio of a non-circular gear pair, (b) is a table | surface which shows ON and OFF of a clutch. It is sectional drawing which shows the structure of a transmission. It is sectional drawing which shows operation | movement of a transmission. It is sectional drawing which shows operation | movement of a transmission. It is a figure which shows typically an example of the dog clutch which is a clutch for non-circular gear element pairs, (a) is a figure at the time of clutch OFF, (b) is a figure at the time of clutch ON. It is a figure which shows the other example of the dog clutch which is a clutch for non-circular gear element pairs, (a) is a fragmentary sectional view at the time of clutch OFF, (b) is a fragmentary sectional view at the time of clutch ON, (c) is ( The sectional view on the AA line of a), (d) is the sectional view on the BB line of (a). It is a figure which shows typically an example of the conventional dog clutch used for the transmission of a motor vehicle, (a) is a figure at the time of clutch OFF, (b) is a figure at the time of clutch ON.

  EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is explained in full detail based on an accompanying drawing.

  First, the basic configuration of the transmission will be described with reference to FIGS.

  As schematically shown in the mechanism diagram of FIG. 1, the transmission 10 includes an input shaft 12 and an output shaft 14 that are rotatably supported, a first gear pair 16, a second gear pair 17, A non-circular gear pair 18 and clutches 40, 42, 44 are provided.

  Each pair of gears 16, 17, 18 is engaged with a pair of gears 20, 30; 22, 32; 24, 34, and there is no delay in the rotation angle. That is, the rotation angle is accurately transmitted and power is efficiently transmitted.

  One gear (input side gears) 20, 22, 24 of each gear pair 16, 17, 18 is fixed to the input shaft 12, and these gears 20, 22, 24 rotate integrally with the input shaft 12. To do.

  On the output shaft 14, the other gears (output side gears) 30, 32, 34 of each gear pair 16, 17, 18 are supported in a relatively rotatable state. The output side gears 30, 32 and 34 are selectively coupled to the output shaft 14 by clutches 40, 42 and 44. That is, when the clutches 40, 42, 44 are ON, the corresponding output side gears 30, 32, 34 are coupled to the output shaft 14, and the coupled output side gears 30, 32, 34 and the output gears are coupled. 14 and rotate together. When the clutches 40, 42, 44 are OFF, the output side gears 30, 32, 34 can rotate relative to the output shaft 14 while restraining the movement of the output shaft 14 in the axial direction.

  When the clutches 40, 42, and 44 are ON, if there is no slippage or the like at the clutches 40, 42, and 44, the output side gears 30, 32, and 34 where the clutches 40, 42, and 44 are ON are changed to the output shaft 14. The rotation angle can be accurately transmitted, and the power can be transmitted efficiently.

  As the clutches 40, 42, 44, it is preferable to use meshing clutches such as dog clutches. In friction clutches such as disc clutches, slipping may occur, whereas in meshing clutches, mechanical structures such as protrusions and holes formed on the drive side and driven side mesh, and friction clutches like This is because slipping does not occur, and if the meshing clutch is used, the rotational angle can be transmitted very accurately and power can be transmitted very efficiently. Although not shown, the clutches 40, 42, and 44 are driven by an actuator, and the operation of the actuator is controlled by a control device. The phase of the non-circular gear pair 18 is detected by a sensor (not shown), and the detection signal is input to the control device. The control device controls ON / OFF of the clutches 40, 42, and 44 so that the reduction ratio can be switched without stopping the rotation, the rotation angle can be accurately transmitted, and the power can be efficiently transmitted.

  Each gear pair 16, 17, 18 is selectively connected between the input shaft 12 and the output shaft 14 by turning on the clutches 40, 42, 44. When the first gear pair 16 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 40, the reduction ratio between the input shaft 12 and the output shaft 14 is relatively large and constant. Reduction ratio RH. When the second gear pair 17 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 42, the reduction ratio between the input shaft 12 and the output shaft 14 is a relatively small constant deceleration. The ratio RL. When the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14 by turning on the clutch 44, at least the reduction ratio between the input shaft 12 and the output shaft 14 is RH and RL. It changes within the range including.

  For example, as shown in FIG. 2, the gears of the gear pairs 16, 17, and 18 are represented by meshing pitch circles (hereinafter simply referred to as “pitch circles”) or meshing pitch curves (hereinafter simply referred to as “pitch curves”). If illustration of the tooth surface is omitted, the first and second gear pairs 16, 17 are circular gears in which the pitch circles 20p, 30p; 22p, 32p of the gears 20, 30;

  The gears 24 and 34 forming the pair of the non-circular gear pair 18 are non-circular gears, and the pitch curve of the gears 24 and 34 forming the pair of the non-circular gear pair 18 is the pitch of the first gear pair 16 having the reduction ratio RH. First sections 25 and 35 equal to the arcs of the circles 20p and 30p, third sections 27 and 37 equal to the arcs of the pitch circles 22p and 32p of the second gear pair of the reduction ratio RL, and the reduction ratio RH And second and fourth sections 26, 36; 28, 38 that vary with the RL. When the gears 24 and 34 forming a pair of the non-circular gear pair 18 rotate in a direction indicated by an arrow in FIG. 2, the sections 25 and 35; 26 and 36; 27 and 37; 28 of the pitch curve of the gears 24 and 34, respectively. , 38 mesh with each other.

  In a situation where the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14, the non-circular gear pair 18 meshes in the third sections 27 and 37 as shown in FIG. In this case, the reduction ratio between the input shaft 12 and the output shaft 14 is RL. As shown in FIG. 2 (b), when meshing in the first sections 25 and 35, the input shaft 12 and the output shaft 14 The reduction ratio during is RH. When meshing in the second sections 26 and 36 and the fourth sections 28 and 38, the reduction ratio between the input shaft 12 and the output shaft 14 changes between RL and RH.

  Next, the operation of the transmission 10 will be described with reference to FIGS. 3 and 4. FIGS. 3A and 4A are graphs of the reduction ratio of the non-circular gear pair 18. The horizontal axis represents the rotation angle of the input shaft 12, and the vertical axis represents the reduction ratio between the input side gear 24 and the output side gear 34. In the tables of FIG. 3 (b) and FIG. 4 (b), the ON state of the clutches 40, 42, 44 is indicated by ◯, and the OFF state of the clutches 40, 42, 44 is blank. 3 (b) and 4 (b), the clutch 40 of the first gear pair 16 having the reduction ratio RH is “clutch (RH)”, and the clutch 42 of the second gear pair 17 having the reduction ratio RL is “clutch”. (RL) ", the clutch 44 of the non-circular gear pair 18 in which the reduction ratio changes is represented as" clutch (shift) ".

  When the clutch 40 of the first gear pair 16 having the reduction ratio RH is ON and the clutches 42 and 44 are OFF, the reduction ratio RH is constant between the input shaft 12 and the output shaft 14. When the clutch 42 of the second gear pair 17 having the reduction ratio RL is ON and the clutches 40 and 44 are OFF, the reduction ratio RL is constant between the input shaft 12 and the output shaft 14. The reduction ratio of the non-circular gear pair 18 changes within a predetermined range including the reduction ratios RH and RL as the input shaft 12 rotates, as shown in FIGS. 3 (a) and 4 (a). In FIGS. 3A and 4A, a curve when the reduction ratio of the non-circular gear pair 18 changes is schematically illustrated.

  When the reduction ratio between the input shaft 12 and the output shaft 14 is changed from RH to RL, the clutches 40, 42, and 44 are operated as follows.

  As shown in FIG. 3A, when the clutch 40 of the first gear pair 16 having the reduction ratio RH is ON, the non-circular gear pair 18 passes through a section 301 where the reduction ratio changes from RL to RH, When entering the section 302 where the constant reduction ratio RH is entered, as shown in FIG. 3B, in addition to the clutch 40 of the first gear pair 16 having the reduction ratio RH, the non-circular gear pair 18 in which the reduction ratio changes. Turn on the clutch 44. Then, after the clutch 44 of the non-circular gear pair 18 is turned on in the section 302 and before entering the section 303 where the reduction ratio of the non-circular gear pair 18 changes from RH to RL, the first reduction ratio RH is set. The clutch 40 of the gear pair 16 is turned off.

  In the section 303 where the reduction ratio of the non-circular gear pair 18 changes from RH to RL, only the clutch 44 of the non-circular gear pair 18 is ON. In the section 303, since the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14, the reduction ratio between the input shaft 12 and the output shaft 14 changes from RH to RL. During this time, if the clutch 44 is not slipped, the rotation angle can be accurately transmitted from the input shaft 12 to the output shaft 14 and the power can be efficiently transmitted by the meshing of the non-circular gear pair 18.

  After passing through a section 303 where the reduction ratio RH of the non-circular gear pair 18 changes from RH to RL and entering a section 304 where the reduction ratio RL is constant, as shown in FIG. 3B, the second reduction ratio RL is set. The clutch 42 of the gear pair 17 is turned on. Then, after the clutch 42 of the second gear pair 17 is turned on in the section 304 and before entering the section 305 where the reduction ratio of the non-circular gear pair 18 changes from RL to RH, the non-circular gear pair 18. The clutch 44 is turned off. Thus, after only the second gear pair 17 is connected between the input shaft 12 and the output shaft 14, the reduction ratio between the input shaft 12 and the output shaft 14 becomes RL constant, and the second By meshing the gear pair 17, the rotation angle can be accurately transmitted from the input shaft 12 to the output shaft 14, and power can be efficiently transmitted.

  Since the clutches 40, 42, and 44 are switched ON / OFF when the driving side and the driven side are at the same speed, a meshing clutch such as a dog clutch can be used as the clutches 40, 42, and 44.

  The same applies to the case where the reduction ratio between the input shaft 12 and the output shaft 14 is changed from RL to RH. That is, as shown in FIG. 4A, after passing through a section 401 where the reduction ratio of the non-circular gear pair 18 changes from RH to RL and entering a section 402 where the reduction ratio RL is constant, FIG. ), The clutch 44 of the non-circular gear pair 18 is turned on in addition to the clutch 42 of the second gear pair 17. Then, after the clutch 44 of the non-circular gear pair 18 is turned on in the section 402 and before entering the section 403 where the reduction ratio of the non-circular gear pair 18 changes from RL to RH, the second reduction ratio RL is set. The clutch 42 of the gear pair 17 is turned off.

  In a section 403 where the reduction ratio of the non-circular gear pair 18 changes from RL to RH, only the clutch 44 of the non-circular gear pair 18 is ON. In the section 403, since only the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14, the reduction ratio between the input shaft 12 and the output shaft 14 changes from RL to RH. During this time, if the clutch 44 is not slipped, the rotation angle can be accurately transmitted from the input shaft 12 to the output shaft 14 and the power can be efficiently transmitted by the meshing of the non-circular gear pair 18.

  After entering the section 404 where the reduction ratio of the non-circular gear pair 18 changes from RL to RH and enters the section 404 where the reduction ratio RH is constant, as shown in FIG. The clutch 40 of the first gear pair 16 is turned on. Then, after the clutch 40 of the first gear pair 16 is turned on in the section 404 and before entering the section 405 where the reduction ratio of the non-circular gear pair 18 changes from RH to RL, the non-circular gear pair 18. The clutch 44 is turned off. In this way, after only the first gear pair 16 is connected between the input shaft 12 and the output shaft 14, the input shaft 12 and the output shaft 14 have a constant reduction ratio RH, and the first By meshing the gear pair 16, the rotation angle can be accurately transmitted from the input shaft 12 to the output shaft 14, and power can be efficiently transmitted.

  Next, a specific configuration example of the transmission 10 will be described with reference to FIGS. As shown in the sectional view of FIG. 5, the input side gears 20, 22, 24 of the gear pairs 16, 17, 18 are fixed to the input shaft 12 in order. On the output shaft 14, the output side gears 30, 32, 34 of the gear pairs 16, 17, 18 are sequentially supported in a state in which relative rotation is possible and axial movement is not possible. Between the output side gear 30 of the first gear pair 16 and the output side gear 32 of the second gear pair 17, a shifter 41 of the circular gear clutch 500 is disposed. The circular gear clutch 500 also functions as both the first clutch for the first gear pair 16 and the second clutch for the second gear pair 17 by also using the shifter 41. . A shifter 45 of the non-circular gear clutch 502 is disposed between the output side gear 32 of the second gear pair 17 and the output side gear 34 of the non-circular gear pair 18. The shifters 41 and 45 of the circular gear and non-circular gear clutches 500 and 502 are slidably supported by spline grooves formed on the output shaft 14, and are movable in the axial direction along the output shaft 14. However, it cannot rotate relative to the output shaft 14 and rotates together with the output shaft 14.

  Grooves 41x and 45x into which actuators (clutch ON / OFF driving means) (not shown) are fitted are formed on the outer peripheral surfaces of the shifters 41 and 45 of the circular gear and non-circular gear clutches 500 and 502. The shifter 41 of the circular gear clutch 500 moves to both sides as indicated by arrows 41 s and 41 t from the intermediate position shown in FIG. 5 by driving an actuator (not shown) fitted in the groove 41 x. The shifter 45 of the non-circular gear clutch 502 moves only one side indicated by an arrow 45t from the standby position shown in FIG. 5 by driving an actuator (not shown) fitted in the groove 45x.

  The shifter 41 of the circular gear clutch 500 has projections (dogs) at a predetermined pitch on the side surface of the first gear pair 16 facing the output gear 30 and the side surface of the second gear pair 17 facing the output gear 32. ) 41a and 41b are formed. The output-side gear 30 of the first gear pair 16 and the output-side gear 32 of the second gear pair 17 have, as constituent elements of the circular gear clutch 500, side surfaces facing the shifter 41 of the circular gear clutch 500, Concave portions (dog holes) 31 and 33 are formed at a predetermined pitch so as to face the protrusions 41 a and 41 b of the shifter 41 of the circular gear clutch 500. When the shifter 41 of the circular gear clutch 500 moves in the direction indicated by the arrows 41 s and 41 t, the protrusions 41 a and 41 b of the shifter 41 of the circular gear clutch 500 are fitted in the recesses 31 and 33 of the output side gears 30 and 32. Then, the output shaft 14 and the output side gears 30 and 32 rotate together through the shifter 41 of the circular gear clutch 500. That is, the first or second gear pair 16, 17 is connected between the input shaft 12 and the output shaft 14, and the output shaft 14 is connected from the input shaft 12 via the first or second gear pair 16, 17. In addition, the rotation angle can be accurately transmitted and power can be transmitted efficiently.

  The non-circular gear clutch 502 is required to finish the meshing ON / OFF operation in a short time, and it is desirable that the clutch is disengaged when an excessive torque is applied to the clutch. Thus, the dog clutch comprised so that it may mesh | engage only by the slope 53a is employ | adopted. The shifter 45 of the non-circular gear clutch 502 is provided with one (driven side) clutch element 52 of the dog clutch on the side surface of the non-circular gear pair 18 facing the output side gear 34. The output side gear 34 of the non-circular gear pair 18 includes a clutch of the shifter 45 of the non-circular gear clutch 502 on the side surface of the non-circular gear clutch 502 as a component of the non-circular gear clutch 502. The other (drive side) clutch element 51 corresponding to the element 52 is provided. When the shifter 45 of the non-circular gear clutch 502 is moved, the clutch element 52 of the shifter 45 of the non-circular gear clutch 502 is engaged with the clutch element 51 of the output side gear 34 of the non-circular gear pair 18 and is non-circular. The output shaft 14 and the output side gear 34 are rotated together through the shifter 45 of the gear clutch 502. That is, the rotation angle can be accurately transmitted from the input shaft 12 to the output shaft 14 and power can be transmitted efficiently.

  The dog clutch, which is the non-circular gear clutch 502, is composed of symmetrical drive-side and driven-side clutch elements 51 and 52 facing each other on the same axis. The clutch elements 51 and 52 are valley-shaped by two adjacent inclined surfaces 53a of the adjacent dog portions 54 by providing a plurality of dog portions 54 having a mountain-shaped convex portion 53 formed of two inclined surfaces 53a along the circumferential direction of the shaft. The concave portions 55 of the driving side clutch element 51 and the convex portions 53 and 55 of the driven side clutch element 51 are formed by alternately forming the convex portions 53 and the concave portions 55 in the circumferential direction. The clutch is configured to be engaged or separated from the clutch 53 and turned on or off. The dog portion 54 is configured by forming a convex portion 53 having a triangular cross section at one end of a dog portion main body 54a having a quadrangular (rectangular) cross section. A gap 56 smaller than the width of the dog body 54a is provided between adjacent dog portions.

  Next, the operation of the transmission 10 will be described with reference to FIGS. As shown in FIG. 6 (a), the shifter 41 of the circular gear clutch 500 moves in the direction indicated by the arrow 41s and engages with the output gear 30 of the first gear pair 16, and the non-circular gear clutch 502. When the shifter 45 is in the standby position, only the first gear pair 16 is connected between the input shaft 12 and the output shaft 14. At this time, as shown by the broken line in the figure, the rotation angle and power are transferred from the input shaft 12 through the input gear 20 of the first gear pair 16, the output gear 30, and the shifter 41 of the circular gear clutch 500. It is transmitted to the output shaft 14 and the reduction ratio becomes RH. When the reduction ratio is switched from RH to RL, first, as shown in FIG. 6B, the shifter 45 of the non-circular gear clutch 502 is moved in the state where the reduction ratio of the non-circular gear pair 18 is RH. The clutch element 51 is moved in the direction indicated by 45t and is engaged with the clutch element 52 of the output side gear 34 of the non-circular gear pair 18, and the first gear pair 16 is interposed between the input shaft 12 and the output shaft 14. Are connected to the non-circular gear pair 18. At this time, as shown by broken lines in the figure, the rotation angle and power are changed from the input shaft 12 to (a) the input side gear 20 of the first gear pair 16, the output side gear 30, and the shifter 41 of the circular gear clutch 500. And (b) the non-circular gear pair 18 is transmitted to the output shaft 14 via the input side gear 24, the output side gear 34, and the shifter 45 of the non-circular gear clutch 502.

  Next, before the reduction ratio of the non-circular gear pair 18 is changed from RH, the shifter 41 of the circular gear clutch 500 is moved to the intermediate position as shown in FIG. The engagement with the output side gear 30 is released, and only the non-circular gear pair 18 is connected between the input shaft 12 and the output shaft 14. At this time, the rotation angle and power are shown from the input shaft 12 through the input side gear 24 of the non-circular gear pair 18, the output side gear 34, and the shifter 45 of the non-circular gear clutch 502, as indicated by broken lines in the figure. Is transmitted to the output shaft 14. Then, with only the non-circular gear pair 18 connected, the reduction ratio of the non-circular gear pair 18 changes from RH to RL.

  Next, when the reduction ratio of the non-circular gear pair 18 becomes RL, the shifter 41 of the circular gear clutch 500 moves in the direction indicated by the arrow 41t as shown in FIG. The second gear pair 17 and the non-circular gear pair 18 are connected to each other between the input shaft 12 and the output shaft 14. At this time, as shown by broken lines in the figure, the rotation angle and power are changed from the input shaft 12 to (a) the input side gear 22 of the second gear pair 17, the output side gear 32, and the shifter 41 of the circular gear clutch 500. And (b) the non-circular gear pair 18 is transmitted to the output shaft 14 via the input side gear 24, the output side gear 34, and the shifter 45 of the non-circular gear clutch 502.

  Next, before the reduction ratio of the non-circular gear pair 18 changes from RL, the shifter 45 of the non-circular gear clutch 502 moves to the standby position as shown in FIG. The fitting with the output side gear 34 is released, and only the second gear pair 17 is connected between the input shaft 12 and the output shaft 14. At this time, as shown by broken lines in the figure, the rotation angle and power are transmitted from the input shaft 12 via the input side gear 22 of the second gear pair 17, the output side gear 32, and the shifter 41 of the circular gear clutch 500. As a result, it is transmitted to the output shaft 14 to reach a constant reduction ratio RL, and the switching of the reduction ratio is completed.

  According to the automobile transmission having the above-described configuration, the non-circular gear clutch 502 includes a dog clutch configured to be engaged only by the inclined surface 53a. Therefore, unlike the conventional dog clutch, the clutch can be engaged in a short time. The ON / OFF operation can be completed, and when an excessive torque is applied, the clutch is disengaged and the transmission including the non-circular gear pair can be prevented from being destroyed.

  FIG. 9 is a view showing another example of a dog clutch that is a clutch for a non-circular gear, where (a) is a partial cross-sectional view when the clutch is OFF, (b) is a partial cross-sectional view when the clutch is ON, and (c) is a cross-sectional view. (A) AA sectional view taken on the line, (d) is BB sectional drawing of (b). As shown in FIG. 9, of the clutch elements on the driving side and the driven side, one clutch element 51 has a dog portion 54 arranged in an outer spline shape, and the other clutch element 52 is arranged in an inner spline shape. 54, and the ridgeline 60 of the convex portion 53 of the dog portion 54 is formed to be inclined at the same angle. The dog clutch of FIG. 9 can achieve the same effects as the dog clutch of FIG.

  As mentioned above, although embodiment thru | or example of this invention has been explained in full detail with drawing, this invention is not limited to the said embodiment thru | or example, Various in the range which does not deviate from the summary of this invention. Design changes are possible. For example, the transmission according to the present invention includes at least three sets of the gear element pairs, at least three sets of the clutches, at least two sets of the non-circular gear element pairs, and at least two sets of the non-circular gear elements. An anti-clutch.

DESCRIPTION OF SYMBOLS 10 Transmission 12 Input shaft 14 Output shaft 16 1st gear pair (1st gear element pair)
17 Second gear pair (second gear element pair)
18 Non-circular gear pair (non-circular gear element pair)
25, 35 First section (first meshing section)
27, 37 Second section (second meshing section)
40 Clutch (first clutch)
42 Clutch (second clutch)
44 Clutch (non-circular gear element pair clutch)
53a Slope 53 Convex part 54 Dog part 55 Concave part 502 Non-circular gear clutch (non-circular gear element pair clutch)

Claims (3)

A first gear element pair and a second gear element pair, which are at least two gear element pairs, each disposed between a rotatably supported input shaft and an output shaft;
A first clutch and a second clutch, which are at least two sets of clutches that releasably connect at least two sets of the gear element pairs between the input shaft and the output shaft;
At least one set of non-circular gear element pairs disposed between the input shaft and the output shaft;
And at least one set of non-circular gear element pair clutches releasably connecting at least one set of the non-circular gear element pairs between the input shaft and the output shaft,
The non-circular gear element pair has a reduction ratio between the input shaft and the output shaft such that the first gear element pair is connected when the first gear element pair is connected between the input shaft and the output shaft. A first meshing section that is equal to a first speed reduction ratio in at least a part of the meshing section of the pair of gear elements, and a speed reduction ratio between the input shaft and the output shaft is determined between the input shaft and the output shaft. And a second meshing section that is equal to a second reduction ratio in at least a part of the meshing section of the second gear element pair when the second gear element pair is coupled between
A transmission comprising a dog clutch configured such that the non-circular gear element pair clutch is engaged with only a slope.   The dog clutch is composed of a symmetric drive element and a driven clutch element facing each other on the same axis, and the clutch element includes a plurality of dog parts having a mountain-shaped convex part composed of two inclined surfaces along the circumferential direction of the shaft. By providing the two inclined surfaces of the adjacent dog portions, valley-shaped concave portions are formed, and convex portions and concave portions are alternately formed in the circumferential direction, and the convex portions and concave portions of the clutch element on the driving side are formed on the driven side. 2. The transmission according to claim 1, wherein the clutch is configured to engage or disengage from a concave portion and a convex portion of the clutch element to turn the clutch on or off.   Of the clutch elements on the driving side and the driven side, one clutch element has a dog portion arranged in an outer spline shape, and the other clutch element has a dog portion arranged in an inner spline shape. The transmission according to claim 2, wherein the ridge lines of the convex portions are inclined at the same angle.

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